EP0609924B1 - Tensioning arrangement - Google Patents

Tensioning arrangement Download PDF

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Publication number
EP0609924B1
EP0609924B1 EP94200039A EP94200039A EP0609924B1 EP 0609924 B1 EP0609924 B1 EP 0609924B1 EP 94200039 A EP94200039 A EP 94200039A EP 94200039 A EP94200039 A EP 94200039A EP 0609924 B1 EP0609924 B1 EP 0609924B1
Authority
EP
European Patent Office
Prior art keywords
cylinder body
locking ring
piston
face
arrangement
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP94200039A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0609924A1 (en
Inventor
Harry David Percival-Smith
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hydra Tight Ltd
Original Assignee
Hydra Tight Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydra Tight Ltd filed Critical Hydra Tight Ltd
Publication of EP0609924A1 publication Critical patent/EP0609924A1/en
Application granted granted Critical
Publication of EP0609924B1 publication Critical patent/EP0609924B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B31/00—Screwed connections specially modified in view of tensile load; Break-bolts
    • F16B31/04—Screwed connections specially modified in view of tensile load; Break-bolts for maintaining a tensile load
    • F16B31/043—Prestressed connections tensioned by means of liquid, grease, rubber, explosive charge, or the like
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
    • B23P19/00—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes
    • B23P19/04—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes for assembling or disassembling parts
    • B23P19/06—Screw or nut setting or loosening machines
    • B23P19/067—Bolt tensioners

Definitions

  • This invention relates to tensioning arrangements and in particular to hydraulically operated bolts or nuts for inducing and retaining tension in studs or bolts or the like.
  • the invention is particularly, but not exclusively, concerned with fastening devices of the type described in UK patent publication GB-A-2245681 in which an annular metal cylinder body is provided with an annular cavity in one end face thereof to receive an annular metal piston the radially inner and outer side walls of which terminate as tapering annular webs which together define an annular recess between them and exhibit such flexibility under hydraulic pressure to seal against the cavity walls whilst the piston is displaced axially along the cavity by hydraulic pressure therein.
  • That device distinguishes from conventional hydraulic nuts by the form of sealing which obviates the necessity for materials which are unable to withstand prolonged exposure to elevated temperatures.
  • the annular metal cylinder body comprises an internally threaded nut body adapted to be threaded onto an elongated bolt or stud protruding from apparatus and the annular metal piston comprises a load ring adapted to bear against the apparatus as the piston and cylinder are separated by hydraulic pressure to induce a tensile stress in the bolt or stud.
  • the piston is part of a piston body which includes a radially outwardly extending flange that faces the part of the cylinder body radially outwardly of the cavity such that shims inserted between said flange and body part maintain the axial juxtaposition, and thus the axial loading, after the hydraulic pressure is removed.
  • a particular use for such a hydraulic nut having the above described sealing arrangement is in a turbine casing where the nut may have to retain tensile loading from casing bolts for many years at elevated temperatures before removal by applying hydraulic fluid pressure, removing the physical retention, that is, displacing the locking ring, and reducing the hydraulic pressure to relieve the tensile loading in the bolt.
  • the spacing pitch of casing bolts is limited by the dimensions of the hydraulic nuts and it is desirable to minimise the radial dimensions. It is convenient to have the locking ring to surround and be supported by the piston body and be displaced axially into abutment with an end face portion of the cylinder body radially outwardly of the annular cavity so that the radial dimensions of the hydraulic nut are effectively defined by the radial dimensions of the annular cavity, dictated by fluid pressure and axial force required to be exerted, and by the radial dimensions of the cylinder body forming walls for the cavity, in withstanding chamber pressure acting radially thereon and the axial tensile loading supported after removal of pressure.
  • the radial thickness of particularly the portion of the cylinder body outwardly of the cavity has been chosen such that any distortion or deflection of the wall due to hydraulic pressure is within its elastic limits so that the wall returns to its original configuration with respect to the piston and seal arrangement when hydraulic pressure is removed. It will be appreciated that where traditional elastomeric sealing arrangements have been used the requirements for return to the precise configuration are less stringent that with the metal web scaling of the above described specification.
  • a hydraulic tensioning arrangement comprises (i) an annular cylinder body surrounding a longitudinal axis and having formed in one end face thereof an axially extending cavity, and which comprises radially outwardly of the cavity a cylinder body wall portion and an end face portion, (ii) an annular piston body having an axially extending annular piston portion which extends into, and forms a sliding fit within, the cavity to define with the cylinder body a fluid chamber, (iii) sealing means for the chamber, (iv) locking means including a locking ring coaxially surrounding the piston body and having a ring end coaxial with, and facing, said end face portion of the cylinder body wall portion, and (v) duct means for supplying liquid at elevated pressure to said chamber to effect, in operation, pressurisation thereof and axial displacement between the piston portion and cylinder body against axial body loading thereon and permit the locking ring means to be located with said locking ring end in abutment with the said end face portion of the cylinder body
  • said end face portion of the cylinder body radially outwardly of the cavity is formed with a substantially complementary slope to said end of the locking ring.
  • a method of inducing and maintaining a tensile stress an elongate member extending from apparatus comprises disposing either one of the cylinder body or piston body coaxially secured to the member such that the other body is supported on the apparatus, supplying liquid at elevated pressure to the chamber to displace the piston body axially with respect to the cylinder body and induce tensile stress in the member, securing the locking ring in abutment with the said end face portion of the cylinder body and against axial movements relative to the piston body, reducing the chamber pressure such that the tensile stress acts between the cylinder body end face portion and the locking ring, and, at least once, repressurising the chamber, securing the locking ring into abutment with said cylinder body face and reducing the chamber pressure.
  • a bolt 10 having longitudinal axis 11 is used to clamp together two parts 12, 13 of apparatus.
  • the bolt has a head 14 arranged to bear against one part 12 of the apparatus and has a threaded shank portion 15 which extends from the other part 13.
  • the apparatus parts 12, 13 are held together in compression by way of a tensile stress induced and sustained in the bolt by a hydraulic nut 16 threaded onto the shank portion and reacted into the part 13.
  • the hydraulic nut 16 is substantially as described in the aforementioned GB-A-2245681, comprising an annular nut body 17 coaxial with the bolt whose radially inner wall 18 is threaded to engage with the bolt and whose lower end face 19 contains an axially extending annular cavity 20.
  • the radially inner and outer walls 22,23 respectively, of the cavity face each other and extend substantially parallel to each other and to the longitudinal axis 11.
  • the nut body by virtue of the cavity 20, comprises a cylinder body.
  • the part 24 of the cylinder body radially outwardly of the cavity may conveniently be referred to as the cylinder body wall portion.
  • An annular piston body 25 comprises a load ring member disposed between the nut body and the apparatus part 13.
  • the load ring includes an optional washer member 25' and an upstanding annular piston portion 26, defined by radially inner and outer side walls 27, 28 respectively, which extends into and forms a sliding fit within the cavity 20 to define, with the cylinder body, a chamber 29.
  • the radially inner and outer side walls 27, 28 of the annular piston portion terminate within the chamber 29 in axially-extending, tapering annular webs 30, 31 which constitute sealing means between the piston and cylinder walls for the chamber.
  • Hydraulic nut locking means includes a locking ring 32 coaxially surrounding the upstanding portion of the piston body and having a ring end 33 coaxial with, and facing, the end face portion 34 of the cylinder body wall portion 24.
  • the locking ring has its radially inner axial wall 32' threaded and is supported by a co-operatively threaded axially extending radially outer side wall 28' of the piston portion axially displaced from said web portion.
  • Duct means 35 including a standard threaded connection port 36, extends through the cylinder body to the chamber 29 to permit hydraulic fluid to be supplied thereto at elevated pressure and vented therefrom.
  • the hydraulic nut device as thus far described is conventional in respect of the elements being known per se within the art.
  • the abutting faces of nut body and locking ring it is conventional for the abutting faces of nut body and locking ring to extend normal to the longitudinal axis 11, in accordance with the present invention, it differs in that the end 33 of the locking ring 32 proximate the cylinder body is recessed to present a radially inwardly sloping face to the end face portion 34 of the cylinder body wall portion 24, that is, radially outward of the cavity 20.
  • the end face portion 34 of the cylinder body is formed with a substantially complementary slope to the end 33 of the locking ring.
  • the recess in the end of the locking ring may conform to part of the surface of a sphere centred on the longitudinal axis, that is, the end face of the ring may have slight curvature in a radial direction, or may conform to part of the surface of a cone centred on the longitudinal axis, that is, the said face of the ring is substantially flat in a radial direction, although any other profile of ring end that is consistent with providing a recess may be employed, within the constraints required of the recess slope as discussed hereinafter.
  • Hydraulic fluid is introduced by way of duct 36 to the chamber 29 at elevated pressure to establish a high pressure within the chamber, both driving the piston web parts 30, 31 into sealing contact with the walls of the cavity and driving the piston an cylinder bodies apart axially, such motion stretching the bolt longitudinally with respect to the apparatus 13 and inducing a tensile stress therein related to the axial force and the fluid pressure whilst correspondingly compressing the parts of the apparatus.
  • the locking ring 32 is displaced axially and secured in abutment with the end face portion 34 of the cylinder body by means of the thread interengagement as show in Figure 2, at which time the pressure in chamber 29 is reduced such that the bolt tensile stress previously supported by way of the base of the cavity and the end of the piston portion is maintained by way of the cylinder body wall portion 24, end face portion 34, locking ring 32 and threaded surface 28' of the piston portion.
  • the recessed ring end permits the end face portion 34 to slide radially inwardly across the face of the locking ring as part of said relaxation of the portion 16' to resume its contacting relationship with the piston web 31.
  • the small recess inclination combines with the load force to generate a small radially inward reaction component on the cylinder body end face portion 34 that encourages, or at least overcomes resistance to, radial movement of the cylinder body wall portion 24 into sealing contact with the piston web 31.
  • the shape of the end face portion 34 does not have to be precisely defined, it will be understood that in order to distribute the axial load uniformly it is desirable that the end face portion conforms in a substantially complementary manner to the recess in the locking ring when both are in an stressed or loaded state.
  • the slopes of the ring recess and the end face portion of the cylinder body may be formed differentially to effect conformity with each other when the ring is under load.
  • the mating surfaces of the ring recess and the face portion of the cylinder body may be caused to conform with each other optionally by bedding-in under load, which process also enables the radial relaxation of the cylinder body portion and sealing efficiency to be ascertained prior to installation.
  • the hydraulic nut may be secured to a bolt with which it is to be used or a dummy bolt, the chamber 29 pressurised to induce a tensile stress in the bolt, the locking ring run along the piston body and secured in abutment with the cylinder body and the chamber vented leaving the bolt tension reacting by way of the cylinder body and face portion 34 and locking ring 32.
  • the cylinder is repressurised and the locking ring repositioned and secured again in abutment with the cylinder body before chamber pressure is reduced and loading between cylinder body and locking ring re-applied.
  • the hydraulic nut may then be reassembled onto a bolt with which to be used and installed to induce and maintain the appropriate tensile stress in the bolt.
  • Such cycling of pressurisation and loading serves to mitigate minor non-conformities between the mating surfaces of locking ring and cylinder body under load and to ensure that the piston webs and cavity walls form an efficacious seal for repeated repressurisation after installation.
  • the hydraulic nut in accordance with the present invention is not limited to that shown in Figures 1 and 2.
  • the annular piston body may be internally threaded to form the nut body for engagement with a bolt 15, and the cylinder body form the load ring resting on the apparatus part 13.
  • a hydraulic nut in accordance with the present invention need not be based upon a structure described in the aforementioned GB-A-2245681 in which the piston body is contained within a cavity defined between radially outer and inner walls of a cylinder body and in which metal webs integral with the piston body provide the sealing means.
  • Figure 3 shows a hydraulic nut 40 which illustrates both a reversal of juxtaposition of piston and cylinder bodies 41, 42 respectively in relation to the bolt 15 and apparatus part 13, as mentioned in the last but one paragraph and a different chamber defining structure, itself well known in the art.
  • the cylinder body 42 has its radially outer side wall 43 axially longer than the radially inner side wall 44 to define cylinder body wall portion 45 and a step-like annular cavity 46 in which the piston body slides.
  • the piston body has its radially outer side wall 47 axially shorter than the radially inner, threaded, side wall 48 and defines an annular cavity 49 of equal radius to that 46, and with annular seals 50, 51 defines fluid chamber 52.
  • Locking means in the form of an internally threaded locking ring 53 is carried on the threaded outer wall of the piston body and faces end face portion 54 of the radially outer body portion 45 of the cylinder body.
  • the locking ring is positionable by rotation about the piston body, when hydraulic pressure in the chamber stresses the bolt, to abut the end face portion 54 of the cylinder body portion 45 and thereafter retained against axial movement by the thread engagement.
  • the end 55 of the locking ring at least, and preferably end face 54 of the cylinder body portion, is recessed to permit radially inward sliding of the cylinder body wall portion over the locking ring face whilst transferring axial loading.
  • a hydraulic device in accordance with the invention is not limited to the threaded locking ring carried by the piston body and moveable into abutment with the end face position of the cylinder body.
  • the locking means 60 comprises a locking ring 62, having a recessed end 63 similar to the ring 32 but unthreaded and freely moveable axially with respect to the axially extending outer side wall of the piston body 26, and a plurality of shims 64 arranged to be disposed about the side wall of the piston body between the locking ring and the apparatus part 13 or washer member 25' as appropriate so that when chamber pressure is reduced axial loading on the cylinder body is transferred by way of the cylinder wall portion 24, locking ring 63 and shims 64 into the apparatus.
  • the locking ring 63 is loosely carried by the end face portion 34 of the cylinder body by way of screws 65, which facilitates disposing the recessed end adjacent the end face portion 34 whilst shims are inserted and no load carried but does not interfere with radial relaxation of the cylinder body wall portion when transmitting load.
  • a hydraulic tensioning arrangement in accordance with the present invention may take a form other than a hydraulic nut, in which the nut body is threaded for securing to a threaded stud or bolt member. It may take the form of a jack in which the annular cylinder body (Figs 1, 2) or piston body (Fig 3) is otherwise secured to apply tension to the member or acts simply as a support for a puller which is internally threaded or otherwise adapted to engage a bolt or the like.
  • the hydraulic tensioning arrangement may take the form of a bolt 70 having a threaded end 71 secured to apparatus part 72 and a shank 73 extending out of apparatus part 74.
  • the bolt head 75 corresponds to the hydraulic nut 16 shown in Figures 1 and 2 except that what was the nut body 17 of those Figures is an integral part of the bolt head. Operation, and the function of the recessed locking ring, is analogous to that described hereinbefore and requires no further description.
  • the bolt head is shown as forming a cylinder body which receives a piston body 76 forming a load ring and carrying a locking ring 77.
  • the end 78 of the locking ring is recessed as is the end face portion 79 of the cylinder body portion radially outwards of the chamber and operation is as described hereinbefore for hydraulic nut 16.
  • the bolt head may be formed as a piston body and the load ring as a cylinder body analogously to Figure 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hand Tools For Fitting Together And Separating, Or Other Hand Tools (AREA)
  • Actuator (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
EP94200039A 1993-02-05 1994-01-11 Tensioning arrangement Expired - Lifetime EP0609924B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9302338A GB2274893B (en) 1993-02-05 1993-02-05 Tensioning arrangement
GB9302338 1993-02-05

Publications (2)

Publication Number Publication Date
EP0609924A1 EP0609924A1 (en) 1994-08-10
EP0609924B1 true EP0609924B1 (en) 1997-03-19

Family

ID=10729951

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94200039A Expired - Lifetime EP0609924B1 (en) 1993-02-05 1994-01-11 Tensioning arrangement

Country Status (5)

Country Link
US (1) US5527015A (ja)
EP (1) EP0609924B1 (ja)
JP (1) JP3542627B2 (ja)
DE (1) DE69402090T2 (ja)
GB (1) GB2274893B (ja)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999046089A2 (de) * 1998-03-09 1999-09-16 Carl Walter Schraubwerkzeug-Fabrik Gmbh & Co. Kg Montageverfahren für zusammenzuspannende platten eines wärmetauschers
WO2004106756A1 (en) * 2003-05-28 2004-12-09 Team Innovation Ltd. Haudralic fastener assembly

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2299641A (en) * 1995-04-05 1996-10-09 Hydraulic Tensioning Technolog Hydraulic tensioning nut
JPH09285926A (ja) * 1996-02-23 1997-11-04 Kyoei Seiko:Kk クランプ装置及び歯車減速装置並びに回転駆動装置
US5927157A (en) * 1996-12-16 1999-07-27 Siemens Westinghouse Power Corporation Axial tensioned bolting system and method thereof
GB9726092D0 (en) * 1997-12-09 1998-02-11 Hydra Tight Ltd Tensioning device
KR20020057738A (ko) * 2001-01-06 2002-07-12 조성은 볼트 신장체결장치
US6763570B2 (en) 2001-11-30 2004-07-20 Westinghouse Electric Company Llc Method of closing a pressure vessel
FI116409B (fi) 2002-02-07 2005-11-15 Metso Paper Inc Kiristyselin
US6840726B2 (en) 2002-12-16 2005-01-11 Siemens Westinghouse Power Corporation Tensioning apparatus and method
US7066699B2 (en) * 2002-12-16 2006-06-27 Siemens Westinghouse Power Corporation Tensioning apparatus and method
DE60334411D1 (de) 2003-02-10 2010-11-11 Atsushi Imai Flüssigkeitsdruckvorrichtung
AU2007221750B2 (en) * 2003-02-10 2008-09-04 Akira Imai Fluid pressure device
CA2457968A1 (en) * 2004-02-19 2005-08-19 Intregra Technologies Limited Hydraulic nut assembly
JP4739320B2 (ja) * 2004-02-25 2011-08-03 ウェントワース バックネル、ジョン 油圧アセンブリ用シール装置
CN100455829C (zh) * 2004-02-25 2009-01-28 J·W·巴克内尔 液压辅助紧固件
KR100621129B1 (ko) * 2004-06-16 2006-09-19 이영식 유공압 너트
US7673849B2 (en) * 2006-02-03 2010-03-09 Integra Technologies Limited Unibody hydraulic nut
CA2632965C (en) * 2008-05-30 2015-11-17 Integra Technologies Ltd. Foundation bolt tensioner
GB2474887B (en) * 2009-10-30 2013-12-04 Stats Uk Ltd Device and method for pre-tensioning a coupling
US8579572B1 (en) 2012-07-23 2013-11-12 Michael James Psimas Load-relief washer assembly for threaded fasteners
WO2014018443A1 (en) 2012-07-23 2014-01-30 Integra Services Technologies, Inc. Load-relief washer assembly for threaded fasteners
US9889529B2 (en) * 2015-05-01 2018-02-13 Riverhawk Company System and method for preloading tension in a stud using an anti-seizure spacer for tapered thread connections
EP3471920B1 (en) * 2016-06-16 2023-01-11 Superbolt, Inc. Improvements to multi-jack tensioners
CN111656025B (zh) * 2017-12-20 2022-02-11 超级螺栓有限公司 多腔室液压的多定位螺栓张紧器
EP3869052A1 (en) * 2020-02-20 2021-08-25 Siemens Gamesa Renewable Energy Innovation & Technology, S.L. Apparatus and method for providing a secure tension connection

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3230799A (en) * 1963-10-23 1966-01-25 Diamond Power Speciality Stud tensioner
US3321182A (en) * 1965-03-26 1967-05-23 Walker Neer Mfg Co Combination hydraulic jack and load holding mechanism
BE788681A (fr) * 1971-09-13 1973-03-12 Westinghouse Electric Corp Mecanisme de fermeture de couvercle pour cuves a pression de reacteurs nucleaires
DE2449009B1 (de) * 1974-10-15 1975-10-09 Schwing Hydraulik Elektronik K Vorrichtung zum Andrehen und Loesen einer von mehreren zum druckdichten Verschliessen eines Reaktordruckgefaesses bestimmten Mutter
ATE108360T1 (de) * 1987-09-29 1994-07-15 John Wentworth Bucknell Krafterzeuger.
GB2245681B (en) * 1990-06-28 1994-01-19 Pilgrim Moorside Ltd Improvements in and relating to fasteners

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999046089A2 (de) * 1998-03-09 1999-09-16 Carl Walter Schraubwerkzeug-Fabrik Gmbh & Co. Kg Montageverfahren für zusammenzuspannende platten eines wärmetauschers
WO2004106756A1 (en) * 2003-05-28 2004-12-09 Team Innovation Ltd. Haudralic fastener assembly

Also Published As

Publication number Publication date
US5527015A (en) 1996-06-18
DE69402090T2 (de) 1997-07-24
DE69402090D1 (de) 1997-04-24
GB2274893B (en) 1995-10-04
GB9302338D0 (en) 1993-03-24
JP3542627B2 (ja) 2004-07-14
JPH06264909A (ja) 1994-09-20
EP0609924A1 (en) 1994-08-10
GB2274893A (en) 1994-08-10

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